Reusable pipe union assembly with automatic fluid flow checking

ABSTRACT

A pipe union assembly with embodiments which are capable of use over a very wide temperature range and which may be cycled through temperatures varying widely from the ambient assembly temperature and also over a wide range of pressures without the need to be retightened. Embodiments of the invention also include structures to automatically check the flow of fluids from the components of the pipe union upon disassembly of the union. The pipe union generally comprises one or more fitting members and a sealing member. The sealing member receives a ridge formed on each fitting member in a sealing fashion. One or more external sleeves hold the fitting member and the sealing member in sealing engagement. The materials from which each fitting member and sealing member are fabricated may be chosen so as to exhibit the proper hardness characteristics and thermal expansion coefficients. A compensating washer is also provided to increase compensation for thermal contractions at low temperatures. Embodiments are provided with restraining clips which are placed in grooves provided on the exterior of the fitting members so as to allow breaking of the sealing engagement and dissipation of any residual pressure before the union is completely disassembled.

RELATED APPLICATIONS

This application is a continuation of U.S. patent application Ser. No.07/399,786, filed Aug. 28, 1989, now U.S. Pat. No. 5,355,908 which is acontinuation-in-part of U.S. patent application Ser. No. 335,149, filedon Apr. 7, 1989, now abandoned which is a continuation application ofU.S. patent application Ser. No. 001,331, filed on Jan. 8, 1987, nowabandoned, which is a continuation-in-part of U.S. patent applicationSer. No. 839,332, filed on Mar. 13, 1986, now abandoned, which is acontinuation-in-part of U.S. patent application Ser. No. 819,948, filedon Jan. 15, 1986, now abandoned. All of the above referenced UnitedStates patent applications are hereby explicitly incorporated herein byreference.

BACKGROUND

1. The Field of the Invention

The present invention relates generally to fittings and couplers for usewith pipes and hoses. More particularly, the present invention relatesto reusable pipe union assemblies which allow two pipes to be repeatedlyjoined together and released from a sealing engagement and whichautomatically checks the flow of fluid when the two pipes are releasedfrom the sealing engagement even under high temperature conditions.

2. The Background Art

In many areas of modern industry, there is an urgent need for deviceswhich allow two pipes are to be repeatedly joined together whileallowing for easy separation of the pipes. This need is especiallyurgent where the pipes subjected to extreme pressure and/or temperatureconditions, including severe changes in temperature, i.e., thermalcycling. The chemical, cryogenic, petroleum, and composite materialsfabrication fields are just some examples of industries having suchneeds.

Although many different devices have been developed in the prior art forjoining pipes, such devices often require cumbersome tightening byunwieldy tools if very high pressures and/or high or low temperaturesare involved. The various devices found in the prior art may be calledConnectors, fittings, unions, couplings, joints, or some other name, butthey all serve the same function of joining two pipes. Furthermore, notonly are many of these prior art devices unsuitable in someapplications, most also pose a safety threat to the operating mechanicassigned to loosen the connective fitting when high pressure isinvolved.

One of the most common methods of joining two pipes involves a flangejoint. Use of the common "flange method" of joining two pipes hasseveral disadvantages. First, it is generally cumbersome and quitedifficult to join two pipes in this way, since many bolts and nuts areoften required. It is important that all of the bolts be tightenedequally. It will be appreciated that properly threading and tighteningall the bolts and nuts on a flange joint can be a cumbersome task. Theamount of time required to assemble or disassemble a flange joint can bea serious disadvantage in many applications.

Other disadvantages of the flange joint include the difficulty ofdisassembly because of the possibility of corrosion and aging of theflanges and ring gasket as well as the number of bolts and nuts whichmust be dealt with. Also, flange joints are subject to leakage whenextremely cold, or extremely hot, fluid is introduced into the jointcausing thermal contraction or expansion. Furthermore, repeated thermalexpansion will often cause the joint to loosen and leak.

Also, in addition to the difficulty accompanying disassembly of thecommon flange joint, the person disassembling the flange joint isexposed to potential harm if any residual pressure remains within thesystem to which the pipes were connected. As a result, personal injurymay occur during disassembly of a common flange joint because the flangejoint does not provide any way of releasing residual pressure beforebeing disassembled. If a method for releasing residual pressure is notprovided, the person disassembling the joint faces the hazardouspossibility that the joint will rapidly separate and spray its contentson the person during the disassembly procedure.

In an effort to overcome some of the above-mentioned difficulties,various devices have been suggested for use as easily assembled and/orreusable, pipe connectors. Among such pipe connectors which have-beendeveloped is one known as a GRAYLOC® connector. While the GRAYLOC®connector is an improvement over the common flange joint, it is stillrelatively difficult to assemble and disassemble, since several boltsand nuts are still required by the clamp structure of the connector.Moreover, there is no assurance that a joint assembled at roomtemperature will remain secure when exposed to thermal cycling at highand low temperatures. Further, the seal ring may need to be replacedeven after a single assembly procedure because of permanent deformationdamage. The GRAYLOC® connector also provides little more protection tothe person disassembling the joint from hazardous residual pressure thandoes the common flange joint.

Another common method of joining two pipes is known as the hammer union.In a hammer union, a first portion of the connector is provided withmale pipe threads on its outer surface with its inner diameter beingprovided with a smooth sloping tapered surface oriented at an angle. Asecond portion of the connector is provided with a sloping taperedsurface to complement that of the sloping tapered surface on the firstportion.

The two tapered surfaces are mated together and an external rotatingsleeve, with female threads, is slipped over the second portion of thepipe and threaded onto the male threads provided on the first portion ofthe connector. The external rotating sleeve, which is provided withridges extending perpendicularly from its external circumference, isstruck with a hammer in order to tighten the joint as much as possible.Thus, the name "hammer union."

The hammer union presents many of the same difficulties that areinherent in the "flange method" of joining two pipes, e.g., difficultdisassembly, frequent inability to reuse the connector, and noprotection from residual pressure remaining in the connector duringdisassembly.

One example of an attempt to provide a more easily assembled anddisassembled pipe connector is known as a HANSEN® coupling. While theHANSEN® coupling has some advantages over other unions, the sealingfunction is provided by a flexible, rubber-like O-ring gasket which isunsuitable for use under extreme temperature or pressure conditions.

Another pipe connector which is an attempt to provide a more easilyassembled and disassembled pipe union is known as a KAMLOK™ connector.The sealing function of the KAMLOK™ connector is provided by a gasket ofrubber-like material. Thus, as with the HANSEN® coupling, the use of aflexible gasket seal makes this connector unsuitable for use in hightemperature or high pressure applications.

An improvement over the above mentioned devices is found in CanadianPatent No. 1,026,791, issued to Krywitsky. The pipe fittings disclosedin the Krywitsky patent are an improvement over the HANSEN® coupling andthe KAMLOK™ connector in that the sealing function is provided by ametal-to-metal interface which allows higher temperatures and pressuresto be contained within the fitting than is possible when flexible,rubber-like gaskets are used.

The fitting disclosed in the Krywitsky patent uses tubular members whichare provided with annular recesses which are defined by relatively thinand flexible lips which serve to carry out the sealing function.Protrusions are forced into the recesses which flex according to thedegree of penetration of the protrusions. Furthermore, as the internalpressure of the fitting increases or decreases, the lips flex somewhathelping to maintain the sealing contact against the protrusion.

Use of the arrangement disclosed in the Krywitsky patent allows the pipefitting to be used in applications involving either a constant high orlow temperature, since the seal is formed by metal-to-metal contact.However, several difficulties are inherent in the design disclosed inthe Krywitsky patent.

First, because the lips of the metallic sealing ring are relativelyflexible, the maximum pressure which may be reliably contained undersome circumstances is limited to about 40 pounds per square inch("psi").

Second, the fitting of the Krywitsky patent may become difficult todisassemble if the fitting lips "seize" onto the protrusion where theprotrusion has been allowed to penetrate into the recess too far. Suchexcessive penetration may be necessary to stop leaking at pressures nearthe maximum allowed for the device.

Third, the sealing structures of the device of the Krywitsky patent mayfail or be subject to damage due to fatigue caused by the flexing of theannular lips.

Fourth, as the annular lips flex, the contact area between theprotrusion and the lips generally decreases. As the protrusion is forceddeeper between the annular lips, the contact area diminishes to a verythin line around the protrusion. Once the contact area has been reducedto such a "point contact," failure of the device may easily occur.

Fifth, as the sealing ring wears because of normal use, the protrusionsmay be allowed to completely penetrate to the bottom of the recesseswhile still not providing a sufficient seal to stop leaking.

Sixth, because the sealing components may be easily damaged and subjectto rapid wear, the reusability of the pipe fitting is uncertain from oneuse to the next.

Seventh, it is nearly always necessary to use tools to assemble ordisassemble the fitting because of the pressure required to force theprotrusion between the annular lips. The fact that tools must always beused decreases the usefulness of the connector. In many applicationsinvolving only moderate pressure, it would be very desirable to providea connector which requires only hand tightening.

Thus, the pipe connector disclosed in the Krywitsky patent is usefulover only a limited range of pressures, and questions of reliabilityarise after the fitting has been properly used only a few times, orimproperly used (e.g., over-tightened), even once.

Still another need which has been unmet in the art is to provide a pipeconnector which automatically halts or checks the flow of fluid throughthe connector when it is disassembled. The automatic checking of fluidflow not only serves an important safety function by preventing theleaking of potentially dangerous fluids from the pipes but alsofacilitates efficiently carrying out many processes in variousindustries. The composite materials fabrication industry is one suchindustry which would benefit from having a connector which automaticallychecks the flow of fluid when disassembled.

None of the above-mentioned devices provides a pipe connector which maybe easily assembled and disassembled and which also maintains a leakproof seal while the device is cycled through a wide range oftemperatures and pressures. Further, none of the devices discussed aboveprovide a pipe connector which provides adequate protection from injuryto the operator due to rapid release of residual pressure contained inthe connector. Still further, none of the devices meet the needs of therapidly expanding composite materials fabrication industry.

In view of the foregoing, it would be an advancement in the art toprovide a pipe union assembly which may be repeatedly used at very lowtemperatures and also at very high temperatures. It would also be anadvancement to provide a pipe union assembly which maintains a fluidtight seal even when subjected to wide thermal cycles i.e., subjected totemperatures that greatly vary from the ambient temperature at the timeof assembly.

It would be another welcome advancement in the art to provide a pipeunion assembly which may be easily assembled without requiringcumbersome tools and which may be hand tightened and still be cycledthrough temperature and pressure changes without requiring subsequentadjustment.

It would also be an advancement in the art to provide a pipe unionassembly which may be subjected to extreme internal pressures and stillmaintain a fluid-tight seal. Still another advancement would be toprovide a pipe union incorporating a structure to allow release ofresidual pressure from the union without causing harm to the persondisassembling the union.

It would be another advancement in the art to provide a pipe unionassembly which could be reused many times without repair or modificationsubsequent to each use. It would be a still further advancement in theart to provide a pipe union assembly which automatically halts the flowof fluid from the pipe whenever the pipe union is disassembled.

BRIEF SUMMARY AND OBJECTS OF THE INVENTION

The pipe union assemblies of the present invention generally comprise atleast one hollow fitting member which may be attached to a pipe, and asealing member which may (in at least one embodiment) be attached toanother pipe. Each fitting member is provided with a tapered ridgerunning perimetrically or peripherally around the end of the fittingmember so as to extend axially therefrom. The sealing member is providedwith at least one perimetric or peripheral tapered channel configured ina shape which complements the shape of the tapered ridge. To provide asealing engagement between the fitting member and the sealing member,the fitting member tapered ridge is inserted into sealing member taperedchannel.

The planar contact between the sides of the tapered ridge and the wallsof the rigid sealing member channel from a fluid tight seal. The taper,or angle, of both the fitting member ridge sides and the complimentarysealing member channel walls are chosen so as to form the most secureseal possible. The components of the pipe union assemblies of thepresent invention are self aligning which makes assembly quick and easy.

At least one external sleeve threadably engages another connectorstructure to hold the tapered ridge into sealing contact with thetapered channel of the rigid sealing member. The walls defining thechannel of the rigid sealing member and the sides of the tapered ridgeof the fitting member may be fabricated from materials which differ intheir hardness by the appropriate amount to provide the maximum sealtherebetween, as will be explained in more detail hereinafter.

In this regard, in one preferred embodiment of the present invention,materials are chosen which have thermal expansion coefficients whichwill cause the sealing engagement between the sides of the tapered ridgeand the walls of the rigid sealing member to be maintained, orincreased, as the temperature of the materials changes from the ambientassembly temperature. In another preferred embodiment, a compensatingwasher is provided to compensate for the decrease in sealing engagementwhich might otherwise be experienced when the assembly is subjected totemperatures much lower than the ambient assembly temperature.

By proper selection of the thermal expansion coefficients of thematerials and inclusion of the compensating washer, a pipe unionassembly is provided which is capable of maintaining a secure seal whensubjected to thermal cycling, i.e., subjected to temperatures that varygreatly from the ambient assembly temperature. This advantage is inaddition to the pipe union being well suited for use at either aconstant high or low temperature.

In yet another preferred embodiment, a restricting means is provided toensure that the union may be disassembled safely even though residualpressure remains in the connector. In still another describedembodiment, structures are provided to check or halt the flow of fluidthrough the pipe union upon disassembly of the pipe union.

It is, therefore, an object of the present invention to provide a pipeunion assembly which may be used at both very low temperatures and atvery high temperatures.

Another object of the present invention is to provide a pipe unionassembly which maintains a fluid tight seal when subjected to thermalcycling, i.e., subjected to temperatures well above and/or well belowthe ambient assembly temperature.

Yet another object of the present invention is to provide a pipe unionassembly which maintains a fluid-tight seal when subjected to internalpressures ranging from at least well below atmospheric pressure to veryhigh pressures.

Another object of the present invention is to provide a pipe unionassembly which may be easily and rapidly assembled or disassembledwithout the use of cumbersome tools and which has a self aligningsealing member.

A further object of the present invention is to provide a pipe unionassembly which may be hand tightened for normal operation and whichmaintains a fluid-tight seal without subsequent adjustment afterassembly even though subjected to widely varying extremes of bothtemperature and pressure.

Still another object of the present invention is to provide a pipe unionassembly which provides a means for releasing residual pressureremaining in the union while protecting the person disassembling theunion from harm.

A further object of the present invention is to provide a pipe unionassembly which may be reused many times without repair or modificationsubsequent to each use.

Yet another object of the present invention is to provide a pipe unionassembly which automatically halts or checks the flow of fluid therefromupon disassembly of the union.

These and other objects and features of the present invention willbecome more fully apparent from the following description and appendedclaims taken in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partially cutaway perspective view of a first presentlypreferred embodiment of the present invention.

FIG. 2 is an elevated cross-sectional view of the embodiment of FIG. 1taken along line 2--2 of FIG. 1,

FIG. 3 is an enlarged view of the portion of FIG. 2. shown circled bythe line 3--3 of FIG. 2.

FIG. 4 is an exploded perspective view of the rigid sealing member andthe two fitting members of the presently preferred embodiment of FIG. 1.

FIG. 5 is a perspective view of one presently preferred embodiment ofthe compensating washer of the present invention,

FIG. 6 is a perspective view of the embodiment of FIG. 1 completelyassembled.

FIG. 7 is a partially cutaway elevated view of the embodiment of FIG. 6.

FIG. 8 is a partially cutaway perspective view of a second presentlypreferred embodiment of the present invention which is similar to theembodiment illustrated in FIG. 1 but which utilizes only a singleexternal sleeve.

FIG. 9 is a partially cutaway perspective view of a third presentlypreferred embodiment of the present invention,

FIG. 10 is an exploded perspective view of the embodiment shown in FIG.9.

FIG. 11 is an elevated cross-sectional view of the embodiment shown inFIG. 9.

FIG. 12 is an elevated cross-sectional view of a fourth presentlypreferred embodiment of the present invention which automatically checksthe flow of fluid upon disassembly of the embodiment.

FIG. 13 is an exploded, partially cutaway perspective view of theembodiment of FIG. 12.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Reference will now be made to the drawings wherein like parts aredesignated with like numerals throughout.

A. A First Presently Preferred Embodiment

Referring first to FIG. 1, a partially cutaway view of one presentlypreferred embodiment of the present invention is shown. This embodiment,generally designated 100 in FIG. 1, includes two hollow fitting members110A and 110B, a hollow sealing member or sealing ferrule 210, twoexternal sleeves 302 and 304 which are shown threaded together, acompensating washer 320 (shown in more detail in FIG. 5), andrestraining clips 326, also sometimes referred to as safety clips 326(shown in FIGS. 6 and 7). Restraining clips 326 are received byrestraining clip grooves 144A and 144B, shown best in FIGS. 1 and 2.

In order to simplify the description of this embodiment, the structuresassociated with fitting members 110A and 110B have been assignedreference numerals from 110 to 144 and also an appropriate A or B letterwhich corresponds to fitting member 110A and fitting member 110B,respectively. Those structures associated with sealing member 210 havebeen assigned reference numerals from 210 to 230, and in some cases arealso designated by an appropriate A or B letter if the structure isparticularly associated with fitting member 110A or 110B.

As seen in FIG. 1, fitting members 110A and 110B are cylindricallyshaped with threads 112A or 112B formed around the inside of theiroutermost ends; these outermost ends are generally designated 114A or114B in FIG. 1. The diameter of fitting members 110A and 110B may beidentical where pipes of identical diameter are to be joined, or may bedissimilar in order to facilitate interfacing with pipes of differentsizes or shapes as will be explained hereinafter.

It should be understood that, as used throughout this disclosure and theappended claims, the terms "pipe" and "pipe member" are meant to includehoses, tubing, and any other conduit-like structure, whether rigid orflexible, used to carry a fluid. Furthermore, the term "fluid" isintended to refer to liquids, gases, or a mixture of both.

Since in the embodiment illustrated in FIGS. 1-7 fitting members 110Aand 110B are identical, the following description will only makereference to fitting member 110A and its associated structures with theunderstanding that the same disclosure also relates to fitting member110B and its associated structures.

The interior cavity, generally indicated at 116A in FIG. 1, of fittingmember 110A is shown as being cylindrical; however, interior cavity 116Aand fitting member 110A may also take on other configurations. Forexample, elliptical or rectangular shaped cavities 116A may be usedaccording to the needs of the particular application.

While the embodiment shown in FIGS. 1-7 is intended to be attached to apipe by threading female threaded portion 112A onto a male threadedportion of the pipe (not shown), other methods for joining each fittingmember to a pipe member may be used. Besides the pipe threads as shownin FIGS. 1-2 and 6-7, other possible methods include high pressure acmethreads, butt welding, or other methods well known in the art.

Whatever method is used to attach a pipe member to fitting member 110A,the seal formed by the connection must have sufficient strength toensure that the connection will not leak or deteriorate when used at theexpected operating temperatures and pressures. In addition, the sealmust also be resistant to the fluid (which in some cases may becorrosive) passed through the pipe union assembly.

The pipe member may be rigidly or even permanently joined to fittingmember 110A, since the need to disassemble the pipe member from fittingmember 110A is typically unnecessary when using the present invention.Thus, the connection between the pipe member and fitting member 110A maybe made by welding to provide additional strength and prevent anyfurther leakage.

Furthermore, the present invention makes interfacing of pipes, tubing,and hoses of different size, shape, and material much simpler than priorart methods. Since fitting member 110A may be easily adapted to acceptthese different pipes, tubing, or hoses at its outermost end 114A, asindicated in FIGS. 1 and 2, the remainder of its structure may befabricated to a standard size. Thus, the present invention greatlyfacilitates the joining of dissimilar pipes without affecting thecompatibility of the interface between fitting member 110A and sealingmember 210.

The material used to fabricate fitting member 110A must be carefullychosen in accordance with four criteria. These criteria for selection ofthe material are: (1) the material must exhibit sufficient strength soas to not be adversely affected when subjected to the temperatures andpressures of the expected operating conditions; (2) the material must beresistant to any corrosive action of the fluid introduced therethrough;(3) the material must have an appropriate thermal expansion coefficient,as discussed below, and (4) the material must have an appropriatehardness, as discussed below.

Fitting member 110A, as shown in FIGS. 1 and 2, may be fabricated fromvarious metals, e.g., carbon steel or stainless steel, which exhibitcharacteristics suitable for the desired application. In thisdisclosure, the hardness of various materials will generally bereferenced to the industry standard Brinell hardness scale (generallyreferenced as "HB=").

As will be appreciated by those skilled in the art of metallurgy, theBrinell hardness number is obtained by indenting the surface of themetal with a hardened steel ball under a load and measuring the averagediameter of the impression by visual observation through a microscope.The measurements provided herein were obtained using Brinell typehardness tester and applying a 3000 Kg load. Using the Brinell hardnessnumber, it is possible to determine the equivalent hardness number onother common hardness scales including the Rockwell, Vickers, and Shorescales by methods well-known in the art.

As can be seen best in FIG. 4, each of fitting members 110A and 110B hasa corresponding peripheral tapered ridge 118A and 118B, respectively, atthe corresponding innermost end 120A and 120B, respectively, of thecorresponding fitting members. The terms "peripheral" and "perimetric"are adopted herewith to describe tapered ridge 118A and tapered channel228A since ridge 118A and 118B are disposed around the perimeter of theinterior cavity formed within fitting member 110A. Thus, peripheraltapered ridge 118A peripherally defines the opening of cavity 116Aformed through fitting member 110A.

Sealing member 210, also referred to as ferrule 210, is provided withtwo peripheral or perimetric tapered channels, generally designated 228A(see FIGS. 2, 3, and 4) and 228B (see FIGS. 2 and 3), each configured toreceive its corresponding peripheral tapered ridge 118A or 118B.Advantageously, sealing member 210 of the present invention is selfaligning in that once tapered ridge 118A is inserted into taperedchannel 228A, no further positioning of sealing member 210 is requiredby the person assembling the union.

Ferrule 210 is preferably shaped so as to match the shape of interiorcavity 116A and the exterior shape of fitting member 110A. Thus, iffitting member 110A is cylindrical, as shown the figures, the shape offerrule 210 is preferably also cylindrical.

FIG. 3 shows the detail of tapered ridge sides 129A which are preferablysmooth, flat, machined surfaces and which are oriented at an angle A tothe central axis of fitting member 110A. In FIG. 3, the broken linemarked C represents the central axis of fitting members 110A and 110Band ferrule 210.

It is preferred that tapered ridge sides 129A, and tapered channel walls230A, be precisely machined to a 32 finish or better. Those skilled inthe art of machining metals will appreciate that the designation "32finish" indicates that the arithmetic mean of the departures from anideally flat surface is equal to only 32 micro-inches. Thus, while avery flat surface may be difficult to obtain, it is generally desirablethat tapered ridge sides 129A be as flat as possible. However, as willbe explained later in connection with the preferred range of hardness ofthe materials used in the embodiment, a surface finish less precise thana 32 finish may be used in some applications.

Angle A may be within the range from about 2° to about. 12°. However,angle A is preferably in the range of from about 5° to about 9° and ismost preferably in the range from about 6° to about 8° in the embodimentshown in FIG. 3. If angle A is too great, for example greater than 12°,it may be difficult to obtain the maximum possible sealing. Generally,as angle A increases, so must the pressure exerted on the fittingmembers to urge them toward the sealing member in order to maintain asecure seal.

If angel A is too shallow, for example less than 2°, damage to ridgesides 129A and channel walls 230A may occur making it difficult todisassemble and reuse the union. Such damage occurs because a bondsimilar to a "cold weld" may occur between tapered ridge sides 129A andtapered channel walls 230A which may result in galling.

It should be appreciated that using angles less than 5° will oftenresult in a more secure seal, but such angles will also potentiallyresult in an embodiment which may be reused fewer times and may also bedifficult to disassemble. However, if the feature of providing a secureseal is paramount to providing a reusable pipe union, angles less than5° may be used. Also, using an embodiment such as that illustrated inFIGS. 12 and 13 utilizing an easily replaceable sealing ring, allows thesofter sealing ring to be discarded if it becomes damaged.

Conversely, the use of angles greater than 9° may potentially result ina less secure seal but may also result in an embodiment Which may beused a greater number of times. In some applications one or the otherconsideration may be paramount. An angle in the range from 6° to about8° has been found to be most preferable for most applications.

Also, for maximum sealing in the embodiments of the present invention,the mating surfaces, ridge sides 129A, and channel walls 230A in FIG. 3should be formed to tolerances which are as close as possible. Forexample, a tolerance of ±1 minute (1/60 of a degree) is desirable.However, if possible, a tolerance within several seconds is morepreferable. The distal end 124A of ridge 118A is preferably straight andflat as shown in FIG. 3.

Thus, when fabricating tapered ridge sides 129A and tapered channel230A, it is necessary to consider the angle of the surfaces, theacceptable deviation, i.e., tolerance, from the chosen angle, and thesurface roughness of the surfaces. It should be appreciated that ifmaximum sealing is to be obtained careful attention must be paid tothese considerations. However, if the embodiment is to be used in lessdemanding applications, less attention needs to be paid to theseconsiderations.

The peripheral tapered channels, generally designated 228A and 228B inFIGS. 2, 3, and 4, located on opposite faces of ferrule 210, are eachprovided with two flat walls 230A and 230B respectively, as shown bestin FIG. 3. Channel bottoms 227A and 227B are preferably smooth and flat.In the following discussion, only the side of ferrule 210 associatedwith fitting member 110A will be described, with the understanding thatthe other side of ferrule 210 associated with the structure of fittingmember 110B is symmetrically identical.

The angle at which channel walls 230A are oriented with respect to axisC is designated A' in FIG. 3. The angle A' must match the angle A oftapered ridge sides 129A within very close tolerances for proper sealingcontact and engagement to occur. Thus, as explained earlier, both anglesA and A' should be within the range of about 2° to about 12°, with therange from about 5° to about 9° being preferable and the range fromabout 6° to about 8° being most presently preferred.

As shown best in FIG. 3, tapered ridge 118A is configured so that theend thereof cannot come into contact with channel bottom 227A. Thus, thenarrowest portion of tapered ridge 118A should not be as narrow as thenarrowest portion of channel 228A.

Due to the foregoing structure, tapered ridge 118A cannot completelypenetrate peripheral channel 228A. However, since the angle A' ofchannel walls 230A and the angle A of ridge sides 129A are essentiallyidentical, a very precise mating occurs between channel walls 230A andtapered ridge sides 129A.

By providing ridge 118A and channel 228A with tapered surfaces, greatersurface area is provided which allows an improved sealing engagementwithout increasing the diameter of the embodiment as is required, forexample, to increase the sealing surface area when using a common flangejoint.

Furthermore, use of a tapered ridge 118A and a tapered channel 228Aadvantageously allows greater pressure to be applied to theridge/channel sealing surfaces. Use of the tapered structures allowsrelatively high pressures to be exerted on the sealing surfaces withoutresorting to tools when assembling the pipe union of the presentinvention. Since sufficient sealing for some applications occurs bytightening the embodiments by hand, tools are often not needed duringassembly or disassembly. However, it may be desirable with someembodiments to use a wrench while assembling the union, or to includehandles on the external sleeves of the embodiment.

In contrast to the "reusable" pipe fittings found in the background art,the present invention achieves a seal by making use of planar sealingsurfaces, comprised of tapered ridge sides 129A and tapered channelwalls 230A. The fittings found in the background art typically rely on apoint or linear contact to effect a seal. By making use of planarsealing surfaces, the present invention is much less affected byimperfections in the sealing surfaces as well as having the otheradvantages mentioned herein.

Importantly, sealing ferrule 210 should be fabricated of a materialwhich has characteristics which will allow it to remain rigid even underthe pressure exerted by the insertion of tapered ridge 118A into taperedchannel 228A. It should be appreciated that the term "rigid" as usedherein is intended to mean that no substantial macroscopic changesoccur.

Furthermore, it is preferable that no macroscopic change occur in eitherfitting member 110A or sealing member 210 after proper assembly of thecoupling. However, it is desirable in some cases that a microscopicchange occur at the mating surfaces of ridge sides 192A and channelwalls 130A as will be explained hereinafter.

As stated earlier, there are also other considerations which should begiven careful attention when choosing a material from which to fabricateferrule 210 and fitting members 110A and 110B. Primarily, theseconsiderations are the thermal expansion characteristics of the materialand the hardness of the material. In one preferred embodiment, ferrule210 is fabricated from aluminum type 7075 and fitting members 110A and110B are made from stainless steel type 304.

Aluminum 7075 possesses a surface hardness 115 Brinell units softer thanstainless steel 304. Also, the coefficient of thermal expansion ofaluminum 7075 is 7.4×10⁻⁶ meters/meter • °C. greater than thecoefficient of thermal expansion of stainless steel 304. The particularimportance played by the coefficient of thermal expansion exhibited bythe material is explained below.

It is often the case that the present invention will be assembled at anambient temperature which may range from -50° C. to +50° C. in someindustrial environments as well as in some harsh naturally occurringenvironments. While some background art devices mentioned earlier wouldhave difficulty maintaining any adequate seal at a temperature of -50°C., none of the known "reusable" devices is able to maintain a secureseal as the temperature of the fitting is significantly elevated above,or reduced below, the "ambient assembly temperature."

Still further, the challenge of maintaining a secure seal is increasedwhen the fitting is subjected to repeated thermal cycling. For example,the pipe union assembly of the present invention may be used at an oilextraction facility near the Arctic Circle. In the winter, suchassemblies may be assembled at temperatures as low as -50° C. and thenexperience a temperature rise of more than 400° C., and pressures above2,000 psi, when steam is passed through the assembly. Alternatively, inother applications the ambient assembly temperature may be 25° C. butthen drop into the cryogenic regions as liquid nitrogen at lower than-190° C. is introduced into the assembly.

As the temperature of the pipe union assembly of the present inventionvaries due to either changing ambient conditions or the temperature ofthe fluid introduced into the pipe union assembly, the components of theunion will undergo thermal expansion or contraction. The case of thermalexpansion or thermal contraction, whichever is to be expected, must beconsidered when designing a pipe union assembly which will be used overgreatly varying temperature conditions.

As can be appreciated by examining the structure shown in FIG. 3, ratherthan incorporating a single sealing surface, two sealing surfaces areprovided on each tapered ridge 118A and tapered channel 228A. Eachtapered ridge 118A is provided with two identical sides 129A and eachtapered channel 228A is provided with two identical walls 230A.

Since one of each of these sides makes sealing contact with acorresponding wall, two sealing surfaces are created by each taperedridge 118A and tapered channel 228A pair. In addition to such attributesas the earlier mentioned planar sealing surfaces, the redundancy ofsealing surfaces is an additional characteristic which allows thepresent invention to provide a seal which is more secure than thatprovided by previously available devices.

The two sealing surfaces will be referred to as the inner sealingsurface, comprising ridge side 129A and channel wall 230A which arenearest the inner cavity of the embodiment, and the outer sealingsurface, comprising ridge side 129A and channel wall 230A which arenearest the exterior of the embodiment. Ideally, the inner sealingsurface will maintain a seal to keep the fluid within the assembly. Ifthe inner sealing surface fails to do so, the outer sealing surface willretain any fluid escaping into channel 228A. Also, the inner diameter ofexternal sleeve 304 fits very closely to the outer diameter of sealingmember 210 as shown in FIG. 3. Thus, external sleeve 304 assists inkeeping the sealing surfaces in engagement with each other under highpressure conditions.

It is desirable, however, that the inner sealing surface be securelymaintained because once fluid escapes into channel 228A, the additionalpressure in channel 228A will tend to push ridge 118A out of channel228A which may increase the possibility of the outer sealing surfacealso failing. Because of the above-explained considerations, if a sealis to be maintained at maximum pressure and at a maximum temperaturedifference, the below described attributes must be incorporated into theembodiment.

As the temperature of the assembly increases there is generally anaccompanying increase in the pressure internal to the union. Thus, astemperature and/or pressure increases it is important that the sealprovided by the mating of channel walls 230A and ridge sides 129A bemaintained or improved. This consideration is met by carefully selectingthe material from which ferrule 210 and fitting member 110A arefabricated so as to meet the strength, rigidity, hardness and thermalexpansion characteristics that are required by the particularapplication.

Importantly, when an embodiment of the present invention must maintain ahigh pressure seal over a wide range of temperatures the thermalexpansion coefficient of the material from which fitting member 110A isfabricated shall be different than the thermal expansion coefficient ofthe material from which ferrule 210 is fabricated.

Referring now to FIG. 4, when the "operating temperature" will besignificantly greater than the ambient assembly temperature, fittingmember 110A should preferably exhibit a higher thermal expansioncoefficient than ferrule 210. Then, as both are subjected to the sameelevated temperature, fitting member 110A will expand to a greaterextent than ferrule 210. Importantly, fitting member 110A will expandboth axially, along line D of FIGS. 3 and 4, and radially, along line Eof FIGS. 3 and 4. Also, the width of tapered ridge 118A will also expandto a greater extent than tapered channel 230A. Thus, as tapered ridge118A expands in the direction indicated by lines D and E, the pressureexerted upon the interface at channel walls 230A and ridge sides 129A isincreased resulting in an improved seal.

When the operating temperature of the assembly will be significantlyless than the ambient assembly temperature, sealing member 210 shouldpreferably exhibit a higher thermal expansion coefficient than fittingmember 110A. Thus, rather than expanding as just explained, sealingmember 210 will contract to a greater extent than fitting member 110Aalong lines D and E shown in FIG. 4. In order to provide the most secureseal when the operating temperature will be lower than the ambientassembly temperature, an additional structure, a compensating washer 320illustrated in FIG. 5, is included. (The use and selection of thecompensating washer will be explained in detail below).

Another primary consideration is the hardness of the material of bothtapered ridge sides 129A and channel walls 230A. Table 1 provides a listof representative materials which may have application in the presentinvention. The values provided in Table 1 were taken from the ASM MetalsReference Book (2d ed. 1983).

It will be appreciated that the values given for both the hardness andthe thermal coefficient of expansion are subject to measurement errorsand will vary slightly with temperature. However, the values provided,which assume a temperature of about 25° C., are useful since thedifference in values between two metals will remain qualitatively thesame as the temperature varies.

                  TABLE 1                                                         ______________________________________                                                                    COEFFICIENT                                                                   OF LINEAR                                                                     THERMAL                                                        BRINELL        EXPANSION                                         METAL        HARDNESS       M · °C.                           ______________________________________                                        CARBON STEEL                                                                  1018         111                11.8 × 10.sup.-6 M                      1020         111                11.7                                          1040         201                12.0                                          1040         514    (Heat Treated)                                                                            12.0                                          4140         302                12.7                                          5160         627                12.6                                          STAINLESS STEEL                                                               303          175                17.2                                          304          175                17.2                                          ALUMINUM                                                                      2011T3       95                 22.6                                          2024         120                22.7                                          6061         65                 24.3                                          7075         60                 24.6                                          ZINC (PLATED)                                                                              76                 27.4                                          COPPER (PLATED)                                                                            44                 16.5                                          ______________________________________                                    

In order to provide the most secure seal possible at the channel/ridgeinterface, channel walls 230A and ridge sides 129A are fabricated ofmaterials which differ in their hardness. In the embodiment shown inFIG. 3, channel walls 230A are fabricated from a material softer thantapered ridge sides 129A. Alternatively, tapered ridge sides 129A couldbe of a material softer than channel walls 230A.

Fabricating sealing member 210 from the softer material is presentlypreferred. While embodiments of the present invention may be used manytimes when properly assembled, should replacement of a part becomenecessary, it is desirable that the replaced part be ferrule 210. Asexplained earlier, fitting member 110A will often be permanentlyattached to a pipe member. Thus, fitting member 110A may be difficult toreplace while ferrule 210 is easy to replace. By making ferrule 210 of asofter material, ferrule 210, rather than fitting member 110A, will bethe component to incur damage due to improper use or wear.

It should be appreciated that the proper "hardness differential" may beaccomplished either by fabricating the entire ferrule 210 or fittingmember 110A of a material having the appropriate hardness, or channelwalls 230A and ridge sides 129A may be plated or coated with appropriatematerial such as zinc or copper as listed in Table 1.

Using the Brinell hardness scale, it has been found that the materialused in ferrule channel walls 230A should have a difference in hardnessin the range of about HB=1 to about HB=300 when compared to the materialused for tapered ridge sides 129A. Desirable results are also obtainedwhen the hardness differential between the two materials is limited towithin the range of from about HB=5 to about HB=200. However, in manyapplications a range of from HB=10 to about HB=150 will be mostpreferred.

As will be appreciated by those skilled in the art, as the hardness of ametal increases, the difficulty of precisely machining the metal alsoincreases. Still, in some high temperature and high pressureenvironments it may be desirable to use very hard metals with or withoutadditional materials plated on the tapered ridge sides or the taperedchannel walls. A general purpose pipe union assembly may have the entirefitting member 110A, including ridges 129A, fabricated of carbon steeltype 1040, while ferrule 210 may have a body fabricated of carbon steeltype 1020.

As stated earlier, ridge sides 129A and channel walls 230A arepreferably formed to a 32 finish or better. In addition to thepreviously discussed reasons, due to the fact that it is nearlyimpossible, and commercially impractical, to form ridge sides 129A andchannel walls 230A to eliminate all surface roughness, it is necessaryto use metals of differing hardness. Since even after precise machiningminute imperfections remain in the surface of ridge sides 129A andchannel walls 230A, the use of metals having differing hardnesses allowsthe softer metal surface to conform to the contour of the harder metalsurface and improve the sealing contact.

It will be appreciated that the conforming of the softer surface occursmicroscopically rather than macroscopically. Thus, no substantial changein dimensions takes place during the sealing process. The conforming ofthe softer surface allows the surfaces to function nearly as well as, oreven better than, perfectly flat surfaces.

It will be realized that the conforming of the softer surface involvesdeformation of the softer-surface. In those cases where the surfaceimperfections are not too great, the deformation will be elastic (i.e.,nonpermanent) deformation. In the case of more severe imperfections, thedeformation can be best described as plastic (i.e., permanent)deformation. When severe surface imperfections are present, plasticdeformation tends to permanently reduce the size of the imperfectionsand thus improve the sealing function during subsequent uses. If thedeformation falls within the elastic range of the softer material, thesurface will repeatedly conform to the harder surface.

It is important that the difference in hardness of the materials not betoo great. For example, channel wall 230A material must not be too muchsofter than the tapered ridge side 129A material. If the channel wallmaterial is too soft, channel walls 230A may undergo too much plasticdeformation resulting in damage during insertion of tapered ridge 118Aand possibly making disassembly and reuse of the union difficult due topermanent macroscopic deformation of the channel wall 230A. Conversely,if channel wall 230A material is not soft enough, the maximum possibleseal will not be formed.

It will be appreciated that in some applications considerations ofproviding a secure seal may outweigh considerations of reusability. Insome circumstances, it may be deemed best to use materials which widelydiffer in their hardness even if it means that the device may only bereused a few times. Alternatively, if reusability is the paramountconsideration, use of relatively hard materials for both fitting member110A and ferrule 210 may be deemed best. However, as the hardnessdifferential between the materials decreases, the pressure which theunion can contain when hand-tightened will decrease. Conversely, as thehardness differential between the two materials increases, a secure sealmay still be attainable by hand tightening.

By carefully implementing considerations of the angle of the sealingsurfaces, the tolerance of the angle, the surface roughness of thesealing surfaces, the hardness exhibited by the sealing surfaces, andthe coefficients of thermal expansion exhibited by the materials, a pipeunion assembly which is reusable many times at extreme pressures andtemperatures, and through repeated thermal cycles, is obtained. Itshould be appreciated that if less than maximum sealing in extremeconditions is all that is required, one or more of the considerationsmay be applied less rigorously.

Male external sleeve 304 and female external sleeve 302, shown in FIGS.1 and 2 and in FIGS. 6 and 7, are provided to align and urge fittingmember ridge 118A into sealing engagement with sealing member channel228A and to secure the resultant seal. In one general purposeembodiment, external sleeves 304 and 302 are fabricated from carbonsteel type 1018. Carbon steel 1018 is a relatively low-cost, easilymachined material having sufficient strength for a general purposeunion.

As seen in FIGS. 2 and 4, each fitting member 110A and 110B has on itsexternal surface an abutting edge, designated 140A and 140B,respectively. Referring to FIG. 2, the external sleeves 304 and 302 areeach formed with corresponding compressing edges, 308 and 306, such thatwhen both male external sleeve 304 and female external sleeve 302 aredrawn together by joining the threads 312 and 310 of the male and femaleexternal sleeves 304 and 302, respectively, tapered ridge 118A is urgedinto sealing contact with tapered channel 228A.

As shown in FIG. 1, external sleeves 302 and 304 are generallycylindrical and have dimensions which allow their inner diameters toslip over the outer diameters of fitting members 110A or 110B andferrule 210 with compressing edges 306 and 308 engaging abutting edges140A and 140B, respectively. Preferably, the fit between the innerdiameter of external sleeves, 302 and 304, and the outer diameters offitting members 110A and 110B and ferrule 210, is a precise one, asshown in FIG. 2, so as to add additional strength to the union 100 bycontacting the outer circumference of ferrule 210 and stabilizing itsposition.

It should be appreciated that structures other than the structures shownin the figures may be devised and used to urge sealing member 210 andfitting members 110A and 110B into sealing engagement.

Optionally, external sleeves 302 and 304 may also be provided with setscrews as shown best in FIGS. 6 and 7 at 330 and 331. Set screw 331,inserted through the threaded bore provided at the circumference of maleexternal sleeve 304 protrudes into ferrule recess 211 but does not makecontact with ferrule 210. In this way, ferrule 210 is "loosely" held incontact with fitting member 110B so as to be held ready for insertion ofridge 118B. Also, since ferrule is held captive by set screw 331, itwill not be misplaced. However, ferrule 210 should still be allowed torotate freely so set screw 331 cannot be inserted too far. It should beappreciated that more than one set screw 331 may be included.

As shown best in FIG. 2, set screws 330 inserted through female externalsleeve 302 preferably engage the end of male external sleeve 304 whichis inserted into female external sleeve 302. Set screws 330, whentightened, prevent the union from being disassembled inadvertently andalso prevent either of external sleeves 302 or 304 from loosening due tovibration.

As explained earlier, the thermal contraction of the components at coldtemperatures must also be considered in order to provide a pipe unionassembly which may be assembled at room temperature but yet stillmaintain a seal when the union is subjected to very low temperatures.Proper selection of a material for fabrication of ferrule 210 andfitting member 110A, e.g., choosing a material having a different(either higher or lower) thermal expansion coefficient for fabricationof fitting member 110A, assists in maintaining a seal when very coldtemperatures are encountered.

Sometimes, however, reliance on thermal contraction of the members maynot be completely effective to ensure that a proper seal will bemaintained when very cold temperatures are encountered. This is becauseaxial contraction of fitting member 110A, along line D of FIG. 4 maycounteract any positive effect of radial contraction. The term oftenused to describe such axial contraction is "creeping."

In order to ensure that a proper seal is maintained when temperaturesfall well below the ambient temperature at the time of assembly, astructure is provided to resiliently urge peripheral tapered ridge 118Ainto sealing member channel 228A. This function is accomplished by acreep-compensating washer 320 shown in the view of FIG. 2 as well as inthe perspective view of FIG. 5.

Washer 320, which is preferably a spring washer, is placed betweenabutting edge 140B of fitting member 110B and compressing edge 308 ofmale external sleeve 304 as seen best in FIG. 2. Alternatively,compensating washer 320 may be placed between abutting edge 140A offitting member 110A and compressing edge 306 of female external sleeve302. Still further, two or more compensating washers 320 can besimultaneously used for additional compensation if desired.

As can be seen in FIG. 5, washer 320 is formed in a conical sectionwhich allows washer 320 to act as a spring. The spring-like structure ofwasher 320 can be seen best in the cross-sectional view of FIG. 2. Thus,as tapered ridges 118A and 118B tend to recede from sealing memberchannels 228A and 228B due to axial thermal contraction (i.e.,"creeping"), compensating washer 320 compensates for this creep byurging tapered ridges 118A and 118B into sealing contact with channelwalls 230A and 230B.

As shown in FIGS. 1 and 2, each of fitting members 110A and 110B arealso provided with grooves 144A and 144B, into which restraining clips326, shown in FIGS. 6 and 7, are placed. Grooves 144A and 144B andrestraining clips 326, also referred to as safety clips 326, serve theimportant function of assisting and protecting the operator during thedisassembly of the pipe union 100. By placing removable restrainingclips 326 in grooves 144A and 144B near the external sleeves 302 and304, restraining clips 326 restrain the unthreading of external sleeves302 and 304.

For example, to disassemble the embodiment shown in FIG. 7, the externalsleeves 302 and 304 are unthreaded from one another until at least onefitting member 110A or 110B is separated from ferrule 210. However,before external sleeves 302 and 304 are completely disengaged from oneanother, each sleeve 302 and 304 is restrained by restraining clips 326placed in grooves 144A and 144B.

As external sleeves 302 and 304 are loosened, the outward pressure onrestraining clips 326 (which are attached to fitting members 110A and110B) force one or both tapered ridges 118A or 118B out of sealingengagement with sealing member channels 228A or 228B. Thus, the sealbetween fitting members 110A or 110B and ferrule 210 is broken beforeexternal sleeves 302 and 304 are completely unthreaded from one another.In this way, restraining clips 326 assist the operator to disassemblethe embodiment.

The restraining effect of the restraining clips 326 serves an importantsafety function in case any residual pressure remains in the pipe unionassembly. If sufficient residual pressure is present, fitting members110A or 110B may be forced out of sealing engagement with sealing member210 as soon as external sleeves 302 and 304 are slightly loosened.However, since external sleeves 302 and 304 are still substantiallythreaded to each other, tapered ridges 118A and 118B and sealing memberchannels 228A and 228B, respectively, are held in close proximity to oneanother and the residual pressure is allowed to escape gradually.

The presence of escaping pressure alerts the operator of the hazardouspressure remaining in the system. By this construction of the presentinvention, an operator is protected from an "exploding" pipe union whichis created when all the restraints on the pipe union assembly arereleased and the internal pressure "blows apart" the union.

The following examples are given to illustrate particular devices andmethods within the scope of the present invention but they are notintended to limit the scope of the present invention.

EXAMPLE 1

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 1 was constructed. The attributesof the subject device were as follows:

Interior Diameter: 1/2 inch

End Fitting Material: 304 SS

Ferrule Material: AL 7075

Angle of Sealing Interface: 8°

The device was hand tightened at about 27° C. and subjected to ahydrostatic test. During the test a liquid was introduced into thedevice at 5000 psi. The test was repeated six times with the devicebeing disassembled and assembled between each test. Importantly, noleaks or pressure drops were detected.

EXAMPLE 2

A device within the scope of the present invention substantially similarto the device described in Example 1 was constructed and tested. Thedevice was hand tightened at a temperature of 49° C. and subjected to ahydrostatic test at 5000 psi as described in Example 1. No leaks orpressure drops were detected.

EXAMPLE 3

A device within the scope of the present invention substantially similarto the device described in Example 1 was constructed. The attribute ofthe subject device which differed from the attributes of the device ofExample 1 was the ferrule material which was AL 2024.

The device was subjected to an experimental field test where it wasrepeatedly assembled and disassembled by hand at room temperature ofabout 25° C. during normal use. During the test, liquid nitrogen atleast as low as -190° C. was conveyed by the device. Even though thedevice underwent repeated thermal cycles of over 200° C., no leaks weredetected.

B. A Second Presently Preferred Embodiment

The major structural features of a second embodiment within the scope ofthe present invention are illustrated in FIG. 8 and are generallydesignated 102. Many of the structures of the second embodiment aresubstantially similar to those discussed in connection with theembodiment illustrated in FIGS. 1-7. While those structures which areclearly similar to previously described structures will not be describedagain, the differences between the two embodiments will be brought outin the following discussion.

The embodiment illustrated in FIG. 8 is configured so that only a singleexternal sleeve is necessary. Fitting member 110B is substantially thesame in both FIG. 8 and FIG. 1; however, male external sleeve 304 andfemale external sleeve 302 have been replaced by single female threadedsleeve 328 illustrated in FIG. 8. Female threaded sleeve 328 engagesfitting member 110B in a fashion similar to that described in connectionwith male external sleeve 304 and fitting member 110B as illustrated inFIG. 1.

Fitting member 110C, and tapered ridge 118C, are substantially identicalto the previously described structures except that fitting member 110Cis provided with threads 148C on its outer circumference. Whenassembled, threads 310 provided on female external sleeve 328, engagefitting member threads 148C. It will be appreciated that by use of asingle external sleeve 328, the fabrication of, and also the use of,embodiment 102 may be simplified.

Fitting member 110B is provided with groove 144B for insertion of arestraining clip. It will be appreciated that the restraining clip (notshown in FIG. 8) still serves the important safety function of breakingthe seal of the assembly before female threaded sleeve 328 may becompletely unthreaded from fitting member 110C.

Fitting members 110B and 110C and female threaded sleeve 328 areprovided with areas which are generally called "wrench flats" 146B,146C, and 332, respectively. The wrench flats are provided in order toallow convenient grasping of the structures of the embodiment by awrench, or other similar tool.

Since the present invention is well adapted for use both in cryogenicand high temperature applications, it is often necessary that the persondisassembling the union must use a wrench or other tool since contactwith the embodiment at extreme temperatures would cause personal injury.As will be appreciated by the foregoing description, even though thepresent invention may form an adequate seal for use at moderatepressures when hand tightened, the same device will contain much higherpressures when tightened using a wrench or a wrench-like apparatus.

The following examples are given to illustrate particular devices andmethods within the scope of the present invention but they are notintended to limit the scope of the present invention.

EXAMPLE 4

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 8 was constructed. The attributesof the subject device were as follows:

Interior Diameter: 1/4 inch

End Fitting Material: 303 SS

Ferrule Material: AL 2011T3

Angle of Sealing Interface: 8°

The subject device was tightened at room temperature to 15 ft. lbs. andsubjected to a hydrostatic test. During the test a liquid was introducedinto the device at 1500 psi and then the pressure was increased by 500psi every 10 minutes until a pressure of 10,000 psi was reached. Nopressure loss or leaks were detected at any time during the test.

EXAMPLE 5

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 8 was constructed. The attributesof the subject device were as follows:

Interior Diameter: 2 inches

End Fitting Material: C1040

Ferrule Material: C1020

Angle of Sealing Interface: 6°

The subject device was tightened at room temperature to 300 ft. lbs. andsubjected to a hydrostatic test. During the test a liquid was introducedinto the device at 6000 psi and then the pressure was increasedgradually until leakage was detected when the pressure reached 9500 psi.When the pressure reached 9500 psi the conventional pipe threads joiningthe fitting members to the pipe members failed thus concluding the test.However, no leakage from the device itself was detected.

EXAMPLE 6

A device within the scope of the present invention substantially similarto the device described in Example 5 was constructed, except the ferrulematerial was C1018.

The subject device was hand tightened at room temperature and subjectedto a hydrostatic test. During the test a liquid was introduced into thedevice at a pressure of 1000 psi. No leaks or pressure drops weredetected, even though the device was hand tightened.

EXAMPLE 7

A device within the scope of the present invention Substantially similarto the device described in Example 5 was constructed.

The subject device was tightened to 300 ft. lbs. at about 26° C. andsubjected to a hydrostatic test. During the test a liquid was introducedinto the device at a pressure of 6000 psi. The device was left for aperiod of 14 hours during which the temperature dropped to 20° C. Atthat time it was noted that the pressure had dropped to 5000 psi. The1000 psi pressure drop corresponds to the drop expected due to thedecrease in temperature. Importantly, no leaks were detected.

EXAMPLE 8

A device within the scope of the present invention substantially similarto the device described in Example 5 was constructed, except the ferrulematerial was C4140.

The subject device was tightened to 300 ft. lbs. at about 25° C. andsubjected to a hydrostatic test. During the test a liquid was introducedinto the device at a pressure of 6000 psi. The device was left for aperiod of 14 hours during which the temperature increased to about 27°C. At that time it was noted that the pressure had increased to 6150psi. The noted pressure increase corresponds to the expected increasedue to the temperature rise. Importantly, no leaks were detected.

EXAMPLE 9

A device within the scope of the present invention substantially similarto the device described in Example 5 was constructed, except the ferrulematerial was C1020 and a coating comprising zinc electroplated to athickness of 5/1000 to 10/1000 inch was provided on the ferrule.

The subject device was hand tightened at room temperature and subjectedto a hydrostatic test. During the test a liquid was introduced into thedevice at a pressure of 2000 psi. At the end of 10 minutes a pressuredrop of 25 psi was noted but no leaks were detected indicating that thepressure drop was due to fluctuations in the test equipment.

EXAMPLE 10

A device within the scope of the present invention substantially similarto the device described in Example 5 was constructed, except the angleof the sealing interface was 8°.

The subject device was tightened at room temperature to 300 ft. lbs. andsubjected to a hydrostatic test. During the test a liquid was introducedat a pressure of 6000 psi. After 12 minutes, the pressure had dropped to4800 psi and a slight leak was detected. It was subsequently determinedthat the surface roughness of the ridge sides and channel walls exceededthe preferred maximum and that this was the cause of the lower thanexpected performance of the device. This example demonstrates theimportance of proper surface roughness if maximum sealing is required.

EXAMPLE 11

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 8 was constructed. The attributesof the subject device were as follows:

Interior Diameter: 2 inches

End Fitting Material: 304SS

Ferrule Material: AL 2024

Angle of Ridge Sides: 8°

Angle of Channel Walls: 10°

The subject device was hand tightened at room temperature and subjectedto a hydrostatic test. During the test a liquid was introduced into thedevice at a pressure of 500 psi. No pressure loss or leakage weredetected after 10 minutes. However, the device failed to contain theliquid at pressures much above 500 psi. This example demonstrates theimportance of properly matching the angle of the ridge sides and channelwalls.

EXAMPLE 12

A device within the scope of the present invention substantially similarto the device described in Example 9 was constructed, except the angleof the sealing interface was 8°.

The subject device was hand tightened at room temperature and subjectedto a hydrostatic test. During the test a liquid was introduced into thedevice at a pressure of 200 psi. No leaks were detected at 200 psi, butthe device failed to contain the liquid when the pressure was increasedmuch above 200 psi. It was subsequently determined that the cause of thelower than expected performance of this device was due to the zincplating provided on the ferrule. The plating was found to be uneven,thus demonstrating the importance of the tolerance of the ridge side andchannel wall angle and also of the proper surface roughness.

EXAMPLE 13

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 8 was constructed. The attributesof the subject device were as follows:

Interior Diameter: 2 inches

End Fitting Material: C1020

Ferrule Material: C1020

Ferrule Coating: Zinc (electroplated 5/1,000 to 10/1,000 inch)

Angle of Sealing Interface: 8°

The subject device was hand tightened at room temperature and subjectedto a hydrostatic test. During the test a liquid was introduced into thedevice at a pressure of 2000 psi. The device initially failed to containthe pressure. However, the device was disassembled and assembled severaltimes and retested. Upon retesting, the device contained a pressure of2000 psi over a period of 10 minutes with no pressure loss or leaks. Itwas concluded that the repeated assembly and disassembly improved thesealing function by reducing the surface roughness of the sealingsurfaces.

EXAMPLE 14

Six devices within the scope of the present invention substantiallysimilar to the embodiment illustrated in FIG. 8 were constructed. Theattributes of the subject devices were as follows:

Interior Diameter: 2 inches

End Fitting Material: C 1020

Ferrule Material: C 1040

Angle of Sealing Interface: 8°

The subject devices were subjected to an experimental field test at aninstallation involved in tertiary recovery of oil by steam injection.The installation was located in northern Alberta, Canada. The deviceswere hand tightened at ambient temperatures as low as -50° C. Steam at350° C. and 2250 psi was then injected into the device. Oil was thenrecovered through the devices at a pressure of 600 psi. The devicesunderwent four steam injection/oil recovery cycles. The devices weredisassembled and reassembled between each cycle. No leaks were detectedduring the test.

EXAMPLE 15

A device within the scope of the present invention substantially similarto the embodiment illustrated in FIG. 8 was constructed. The attributesof the subject devices were as follows:

Interior Diameter: 1/4 inch

End Fitting Material: 304SS

Ferrule Material: AL 2024

Angle of Sealing Interface: 8°

The device was subjected to an experimental field test where it wasrepeatedly assembled and disassembled at room temperature by hand duringnormal use. During the test, liquid nitrogen at least as low as -190° C.was conveyed by the device. Even though the device underwent a thermalcycle of over 200° C., no leaks were detected.

C. A Third Presently Preferred Embodiment

A third presently preferred embodiment within the scope of the presentinvention is illustrated in FIGS. 9-11 and is generally designated 104.FIG. 9 is a partially cutaway perspective view of this third preferredembodiment. Many of the structures incorporated into the thirdembodiment shown in FIG. 9-11 are very similar, or identical, to thestructures used in the first embodiment previously described.

The embodiment shown in FIG. 9 includes one fitting member 410 and onesealing member 510. Fitting member 410 is provided with a tapered ridge418 running perimetrically around the innermost end of fitting member410 in a manner similar to tapered ridge 118A or 118B of the previouslydescribed embodiment. Sealing member 510 is provided with taperedchannel 528 running parametrically around the innermost end of sealingmember 510.

One female external sleeve 350 is provided with compressing edge 358which biases compensating washer 320 against abutting edge 440 offitting member 410. Sleeve 350 attaches to the external surface ofsealing member 510 in a manner to be described in more detailhereinafter.

This third embodiment has fewer components than the previously describedfirst embodiment and may be used in many of the same applications as thepreviously described embodiment. However, it is best suited for use inapplications involving lower pressures and little thermal cycling. Forexample, as suggested by FIGS. 9-11, the embodiment may be used forproviding an efficient union for connecting hoses, such as low pressurehydraulic hoses or water hoses. This third embodiment, is easier andless expensive to manufacture because of fewer components and is thusalso easier to assemble and disassemble.

As shown in the perspective view of FIG. 9, the third embodimentincludes fitting member 410 which is similar in construction to fittingmember 110A or 110B of the first embodiment. Fitting member 410, asshown in FIG. 9, is provided with male threads 412 for connectingfitting member 410 to hose 12 by way of hose fitting 14, shown in FIG.9.

Similar to the first embodiment, fitting member 410 of the thirdembodiment is provided with tapered ridge 418. However, only one fittingmember and only one external sleeve (instead of two) are used to formthe seal in the third embodiment. Thus, the third embodiment may befabricated at a significantly lower cost than the first embodiment.

The considerations discussed above in connection with forming anadequate seal in the first embodiment, particularly regarding the angleof tapered ridge sides 429, and the materials from which fitting member410 is fabricated, are substantially the same for this third embodiment.

For example, referring to FIG. 11, the angle of tapered ridge sides 429in relation to the fitting member central axis is preferably within therange of about 2° to about 12°, with the most presently preferred valuebeing about 8°. Furthermore, the hardness differential between thematerial comprising tapered ridge sides 429 and sealing member channelwalls 530 should be within the range of about 1 to about 300 Brinellunits with the most presently preferred differential being from about 10to about 150 Brinell units. Still further, as discussed in detail withrespect to the first embodiment, fabricating fitting member 410 andsealing member 510 of materials having different temperature expansioncoefficients will also promote proper sealing of the second embodimentwhen thermal cycles are encountered.

Since the third embodiment is primarily contemplated for use inapplications involving less severe temperatures and pressures than thefirst embodiment, consideration of all of the features used in the firstembodiment may not be necessary in order to provide for proper sealingin the practical operation of the second embodiment.

As explained above, the angle at which tapered ridge sides 429 andchannel walls 530 are oriented is preferably in the range from about 6°to about 8°; however, tolerances need not be close if the embodiment isused in only low pressure conditions.

Furthermore, if the temperatures and pressures which the thirdembodiment is subjected to are not extreme, the considerations relatingto the hardness differential and the thermal expansion coefficients ofthe components may be applied less rigorously than with the first orsecond embodiment. For example, in some low pressure and stabletemperature situations, it may not even be necessary to use materialshaving a hardness differential or having different thermal expansioncoefficients in order to provide a proper seal.

Sealing member 510 of the third embodiment, as illustrated in FIG. 11,differs from sealing member 210 of the first embodiment in that hose 10of the third embodiment is connected directly to sealing member 510 byway of a threaded connection between hose fitting 16 and sealing memberthreads 512. A gasket 22 may also optionally be provided. The sealingmember tapered channel, generally designated 528 in FIG. 10 and alsoshown in FIG. 10, is preferably structured using the same considerationsas discussed in connection with sealing member 210 of the firstembodiment.

In the third embodiment, both fitting member 410 and sealing member 510may be fabricated of materials corresponding to the materials from whichthe fitting member and sealing member are fabricated in the firstembodiment. However, if the operating conditions do not involve extremetemperatures and pressures, it will be appreciated that the thirdembodiment may be fabricated of materials such as plastics or othermaterials which are easily molded or machined.

FIG. 10 represents an exploded perspective view of the embodiment shownin FIG. 9. FIG. 10 shows tapered ridge 418, sealing member taperedchannel 528 and interior cavity 516 of sealing member 510. The outersurface of sealing member 510 which is preferably cylindrical, isprovided With three substantially L-shaped grooves, generally designated540 (two of which are shown in FIG. 9) which allow the third embodimentto be rapidly assembled or disassembled.

Each groove 540 receives a corresponding external sleeve pin 354 whichis mounted to the interior surface of external sleeve 350, the interiorsurface of sleeve 350 being preferably cylindrical and of substantiallythe same diameter as the outer surface of sealing member 510. The pin354 and groove 540 arrangement allows the embodiment to be quicklyassembled or disassembled by essentially twisting the external sleeveand fitting member in opposite directions; this groove and pinarrangement has thus been termed a "quick twist coupling."

As can be seen best in FIG. 10, grooves 540 are provided with a firstportion 542 which is widened so as to form a mouth to easily receive pin354. Groove 540 is also provided with a second portion 544 which issubstantially perpendicular to the end of sealing member 510 and whichallows pin 354 to travel freely for a distance before contacting a thirdportion 546 which preferably forms an angle greater than 90°, preferablyabout 96°, with second portion 544. Groove 540 terminates with recess548 which serves to lock pin 354 in place.

Once pin 354 is inserted through first groove portion 542 and intosecond groove portion 544 so as to contact the junction between grooveportion 544 and 546, sealing member 510 and fitting member 410 arerotated in opposite directions such that each pin 354 slides along thethird portion 546 of its respective groove 540. Since third grooveportion 546 is oriented at an angle of about 96° from second grooveportion 544, external sleeve 350 moves radially towards sealing member510 and is "pulled onto" sealing member 510 as they are rotated to movepins 354 along third groove portions 546.

To make best use of the quick twist coupling feature of the thirdembodiment, it is preferable that tapered ridge 418 and tapered channel528 first make sealing engagement when pins 354 are situated somewherewithin the third groove portion 546 which is indicated by the bracketmarked S. By positioning pins 354 and grooves 540 such that sealingengagement occurs when pins 354 are in the area marked S provides for amore secure seal and provides for a mechanism to subsequently break theseal as will be explained in more detail hereinafter.

The recess 548 located at the end of each third groove portion 546serves to secure its respective pin 354 in place once pin 354 reachesrecess 548. With grooves 540 being structured as described herein,tapered ridge 418 and tapered channel 528 are held in sealing engagementonce pins 354 are locked into recesses 548 of grooves 540.

FIG. 11 is a cross-sectional view of the third embodiment shown in FIG.9. Compensating washer 320 shown in FIG. 11 may be identical tocompensating washer 320 shown in FIG. 5. Compensating washer 320, shownbest in FIG. 11, serves a dual purpose in the third embodiment. Asdiscussed previously in connection with the first embodiment,compensating washer 320 serves to provide compensation due to "creeping"(degradation of the seal due to thermal contraction) which occurs at lowtemperatures.

Importantly, compensating washer 320 in the third embodiment also servesto bias external sleeve 350 in a direction which will hold pins 354 ingroove recesses 358 and thus provides the tension necessary for properoperation of the quick twist coupling. In this regard, when pins 354 areseated in groove recesses 358, washer 320 biases fitting member 410towards sealing member 510, and thus assists in forming a proper seal.

As can be seen best in FIG. 11, fitting member 410 is provided with anabutting edge 440 while external sleeve 350 is provided with acompressing edge 358. One pin 354 and one groove recess 548 can be seenin the lower portion of FIG. 10. Compensating washer 320 is positionedso that external sleeve compressing edge 358 and abutting edge 440 areurged apart. Pins 354, grooves 540, and compensating washer 320, arearranged such that sealing contact between tapered ridge 418 and taperedchannel 528 occurs when pins 354 are situated in third groove portion546 which is designated S in FIG. 10. This arrangement provides thatwhen pins 354 are received in groove recesses 548 shown best in FIG. 10,compensating washer 320 is partially or fully compressed.

By the above-described arrangement, fitting member ridge 418 is held intight sealing arrangement with sealing member channel 528. When pins 354are received in groove recesses 548, compensating washer 320 must becompressed even further to release the tension on pins 354 and removepins 354 from recesses 548. When the third embodiment is disassembled,tapered ridge 418 and tapered channel 258 will be forced from sealingengagement once pins 354 pass through the area of third groove portion546 which is designated S. Thus, the configuration of grooves 540 helpsto break the seal when the external sleeve 350 and sealing member 510are counter-rotated to disassemble the union.

It should be understood that compensating washer 320 may be replaced bystructures other than that shown and described in connection with FIG.11 above. For example, if the embodiment is to be used only undermoderate temperature and pressure conditions, compensating washer 320may be a washer of a resilient material, such as rubber. Depending uponthe application, those skilled in the art will be able to determine whatalternative structures and materials may be used for compensating washer320.

The most important criteria when selecting a material for compensatingwasher 320 is that washer 320 must be compressible so as to allow pins354 to seat in groove recesses 548 while urging fitting member ridge 418into sealing engagement with sealing member channel 528. Thisarrangement provides a coupling which is highly resistant to looseningdue to vibration. Thus, when the above-described quick-twist couplingfeature is used, there is often no need to include set screws,such asthose shown in FIGS. 2 and 11 at 330.

The following examples are given to illustrate particular devices andmethods within the scope of the present invention but they are notintended to limit the scope of the present invention.

EXAMPLE 16

A device substantially similar to the embodiment illustrated in FIG. 9was constructed except a threaded external sleeve was used rather thanthe "pin and groove" arrangement shown in FIG. 9. The parameters of thesubject device were as follows:

Interior Diameter: 2 inches

Fitting Member and Sealing Member

Material: C1020

Angle of Sealing Interface: 6°

The subject device was tightened to 300 ft. lbs. at room temperature andsubjected to a hydrostatic test. During the test a liquid was introducedinto the device at a pressure of 6,000 psi. After a period of 40 minutesno loss of pressure or leaks were detected.

EXAMPLE 17

A device substantially similar to the embodiment illustrated in FIG. 9was constructed except a threaded external sleeve was used rather thanthe "pin and groove" arrangement shown in FIG. 9. The attributes of thesubject device were as follows:

Interior Diameter: 2 inches

Fitting Material: C1020

Sealing Member Material: C1020 provided with a zinc plating 5/1000 to10/1000 inches thick

Angle of Sealing Interface: 8°

The subject device was hand-tightened at room temperature using handles4.5 inches long attached to the external sleeve of the device, andsubjected to a hydrostatic test. During the test, a liquid wasintroduced into the device at a pressure of 2,500 psi. While the devicefirst failed to contain this pressure, it contained this pressure afterit was disassembled and reassembled several times and then retested. Itwas subsequently determined that the repeated assembly and disassemblydecreased the surface roughness (i.e., improved the surface finish) ofthe ridge sides and the channel walls thus improving the seal.

F. A Fourth Presently Preferred Embodiment

FIGS. 12 and 13 illustrate a fourth presently preferred embodiment ofthe present invention, generally referred to at 106. As done previouslyin this disclosure, in order to simplify the description of thisembodiment the structures associated with fitting members 610A and 610Bhave been provided with an appropriate A or B letter which correspondsto fitting member 610A and fitting member 610B, respectively. Also, someillustrated structures associated with sealing member 710 have beendesignated by an appropriate A or B letter if the structure isparticularly associated with fitting member 610A or 610B.

FIG. 12 is an elevated cross-sectional view of a fourth presentlypreferred embodiment within the scope of the present invention which isparticularly adapted for use in applications where fluid flow throughthe pipes connected to the union must be checked whenever the unionassembly is disassembled. In the embodiment of FIG. 12, structures areprovided which automatically check the flow of fluid through each of thefitting members whenever the union is disassembled.

The flow checking function of the embodiment illustrated in FIGS. 12 and13 is particularly advantageous in many applications. For example,automatically halting the flow of fluid, either a liquid or a gas, froma fitting member upon disassembly of the embodiment may serve asignificant safety function. Such may be the case when a hightemperature fluid under pressure is flowing through the pipe unionassembly and an operating mechanic might be injured if significantcontact with the fluid were to occur.

The flow checking function of the embodiment illustrated in FIGS. 12 and13 also solves problems that have been faced in various industries. Forexample, when fabricating structural parts of various kinds usingcomposite materials, particularly advanced composite materials usingexotic fibers bonded into a resin matrix, it is often necessary tovacuum seal the composite part against a positive mold using anair-tight collapsible vacuum bag.

Once the composite materials have been placed in a mold, a vacuum bag isplaced around the bag and after the part has attained it finished shape,all of the gases are evacuated from the bag. The bag and the compositematerial contained therein is then placed in an autoclave and subjectedto high temperatures, often 600° C. and above, to cure the material.Creating and then maintaining a vacuum within the bag at the hightemperatures experienced in an autoclave has posed a significant problemwhen using prior art devices.

By using the embodiment of FIGS. 12 and 13 the problems experienced withthe prior art devices are alleviated. In use, the present invention isconnected to the bag and then to a vacuum supply line. After theinterior of the bag has reached the proper pressure, an operatingmechanic merely disassembles the pipe union assembly. The portion of thepipe union assembly connected to the bag automatically seals the vacuumwithin the bag and the portion of the assembly connected to the vacuumsupply line automatically seals the supply line. Importantly, theportion of the pipe union which is attached to the bag remains attachedand seals the vacuum within the bag throughout the high temperaturecuring process.

Significantly, since the curing step of composite materials is carriedout at high temperatures, the all metal construction of the embodimentof FIGS. 12 and 13 allows the embodiment to withstand the hightemperatures of the curing step. Not only does the fourth embodimentmaintain a secure seal while undergoing the severe temperature changesand thermal cycling, but the embodiments may also be repeatedly used.The ability to withstand high temperature while maintaining a seal andto be repeatedly used in such applications is a great advantage overpreviously available devices. Thus, the embodiment of FIGS. 12 and 13provides a significant advance over the prior art in the area ofcomposite materials fabrication and other areas having similarrequirements.

Importantly, the embodiment illustrated in FIGS. 12 and 13 may be usedto applications utilizing either negative pressures (i.e., a vacuum) orpositive pressures (i.e., pressures above atmospheric pressure).

Referring now to the cross-sectional view of FIG. 12, the principlestructures of the fourth embodiment will be explained. As was the casewith several of the previously described embodiments, the fourthembodiment includes two fitting members 610A and 610B which share somesimilar structures. The differences between the two fitting members willbecome apparent in the following description. It will be appreciatedthat the features of the embodiment represented in FIGS. 12 and 13 maybe incorporated into other embodiments of the present invention, forexample, those including only one fitting member and one sealing member.

Importantly, the earlier described considerations regarding thefabrication of the sealing surfaces and the materials from which thecomponents are constructed apply in the embodiment of FIGS. 12 and 13also. Such considerations include the angle of the sealing surfaces, thesurface roughness of the sealing surfaces, tolerance of the sealingsurface angle, the hardness differential of the sealing surfaces, thecoefficient of thermal expansion of the union components, as well asother considerations.

As represented in FIG. 12, two fitting members 610A and 610B are insealed engagement with a sealing member or sealing ferrule 710. At afirst end of each of fitting members 610A and 610B, pipe threads 612Aand 612B, respectively, and wrench flats, 613A and 613B, respectively,are provided to allow fitting members 610A and 610B to be attached topipes (not shown in FIG. 12). Pipe threads 612A and 612B arerepresentative of the many structures which may be used to provide ameans for attaching the fitting member to a pipe member.

Also represented in FIG. 12 is a single external sleeve 650. The singleexternal sleeve 650 functions to press tapered ridges 628A and 628B ofthe fitting members 610A and 610B into sealing engagement with thecorresponding tapered channels 712A and 712B of sealing member 710 ashas been explained previously in connection with other embodiments ofthe present invention. The internal circumference of one end of theexternal sleeve 650 is provided with threads 624 which engage threads622 provided on the external circumference of fitting member 610A.

It should be appreciated that an important feature of all theembodiments if the present invention is the ability of the embodimentsto be reused many times. Particularly in the case of the embodimentillustrated in FIGS. 12 and 13, the ability to function in the hightemperature environment of an autoclave and also be reused many times isa great advantage not obtainable from previously available devices.

As external sleeve 650 is threaded onto fitting member 610A, a footportion, indicated at 629 in FIG. 12, of external sleeve 650 compressesa compensating washer, illustrated at 620. Compensating washer 620,which functions similarly to the compensating washers associated withearlier described embodiments, is pressed against an abutting edge,shown at 632, formed on fitting member 610A. In this way, fittingmembers 610A and 610B are pressed into contact with sealing member 710.

As discussed previously in connection with the first embodiment,compensating washer 620 serves to provide compensation due to "creeping"(degradation of the seal due to thermal contraction) which occurs at lowtemperatures. Wrench flats 631 are provided on external sleeve 650 incase it is desirable to use a tool to loosen the pipe union assembly dueto the high or low temperature of the union.

As similarly described in connection with the previously illustratedembodiments, a restraining clip, 626 in FIG. 12, is provided to ensurethat the seal between one of the fitting members and sealing member 710is broken before external sleeve threads 624 are disengaged from fittingmember threads 622. Restraining clip 626 also serves to keep fittingmember 610B and external sleeve 650 together when the embodiment ofFIGS. 12 and 13 is disassembled.

Still referring to FIG. 12, set screws 630 are threaded into boresprovided in external sleeve 650 so they loosely extend into sealingmember recess 720 but so they do not make actual contact with sealingmember 710 after assembly of the embodiment. In this way, sealing member710 is "loosely" held in contact with fitting member 610B so as to beheld ready for alignment and insertion of tapered ridge 628B intotapered channel 712B. Also, since sealing member 710 is held looselycaptive by set screws 630, it will not be misplaced when the embodimentis disassembled. However, sealing member 710 should still be allowed torotate freely during use so set screws 630 should not be inserted toofar.

Further represented in FIG. 12 are those structures which function as acheck means for halting the flow of fluid through the respective fittingmember. By way of example and not by limitation, check balls 620A and620B, springs 618A and 618B, spring retaining ring 616A and 616B, springretaining clip 614A and 614B, and ball seats 630A and 630B, function asa check means in the embodiment illustrated in FIGS. 12 and 13. Thecheck balls and the ball seats also function together as a valve means.The springs illustrated in FIGS. 12 and 13 function as a biasing meansto ensure that the valve formed by the check balls and ball seats isnormally closed.

As explained earlier, the embodiment of FIGS. 12 and 13 allows fluid toflow through the union assembly when the two fitting members 610A and610B are both in sealing engagement with the sealing member 710. Thus,associated with sealing member 710 is a disable rod 716 which in theillustrated embodiment functions as a means for disabling the fluidchecking function of check balls 620A and 620B.

As shown in FIG. 12, by way of example and not by limitation, when theembodiment is assembled, a fluid path is established through fittingmember 610A, past check ball 620A, through the plurality of bores 714provided in sealing member 710, past check ball 620B, and throughfitting member 610B.

The concave shape of the end of the disable rod can be seen best in FIG.13. It will be appreciated that the length of disable rod 716 may bevaried to increase or decrease the cross sectional area of the fluidflow path or to vary the speed at which the flow of fluid is checkedwhen the union is disassembled.

Referring now to FIG. 13, an exploded, partially cut-away perspectiveview of the fourth presently preferred embodiment is provided. Asillustrated in FIG. 15, when the pipe union is disassembled, check balls620A and 620B are pressed into their respective ball seats (630A and630B in FIG. 12) by springs 618A and 618B to halt the flow of fluidthrough fitting members 610A and 610B. Ball seats 630A and 630B areformed to provide a fluid tight seal in cooperation with check balls620A and 620B.

As shown best in FIG. 13, sealing member 710 is provided with aplurality of bores 714 which provide a fluid flow path through thesealing member. Also provided in sealing member 710 is a rod guide bore,shown at 718, into which disable rod 716 is inserted. The rod guide bore718 serves to properly position disable rod 716 against the check balls.

In use, the embodiment illustrated in FIGS. 12 and 13 provides manyheretofore unavailable advantages. For example, after the fittingmembers 610A and 610B have been attached to pipe members, fluid may beintroduced into the pipe members and no leakage will occur through thefitting members because check balls 620A and 620B are firmly heldagainst ball seats 630A and 630B, respectively, when the pipe union isdisassembled (as shown in FIG. 13.

When it is desired to halt the fluid flow through the pipe union, it ismerely necessary to begin to disassemble the pipe union. As the externalsleeve (650 in FIG. 12) is unthreaded, the fitting members will beseparated from the sealing member and, depending on the length of thedisable rod (716 in FIG. 13) the check balls will once again firmly reston their respective ball seats checking the flow of fluid through thefitting members.

Those having skill in the pertinent arts will readily be able tofabricate or obtain components which will serve the above describedpurposes and functions, or slightly different purposes and functions,which are within the scope of the present invention. It is expected thatthe many different embodiments within the scope of the present inventionmay fabricated to serve in particular applications.

EXAMPLE 18

A device substantially similar to the embodiment illustrated in FIG. 12was constructed. The parameters of the subject device were as follows:

Interior Diameter: 1/2 inch

Fitting Member

Material: 304SS

Sealing Member

Material: Brass 360

Check Balls: Stainless steel

The subject device was attached to a collapsible bag containing a baggedcomposite material structural part. The subject device was alsoconnected to a source of vacuum and the gases in the bag were removed.Once a vacuum was achieved in the bag, the bag and the attached portionof the subject device were placed in an autoclave and subjected to atemperature of 670° C. at 190 p.s.i. for 24 hours. The autoclave wasthen cooled to approximately ambient temperature and the temperature andpressure was again increased. The cooling and heating cycle of theautoclave was repeated once more. The bag was then removed from theautoclave and the loss of vacuum from within the bag was measured. Theloss of vacuum which occurred when using the subject device was only0.005 inches of Hg per minute.

When prior art devices were subjected to this test, a vacuum loss ofover 8.55 inches of Hg per minute was generally experienced.

As will now be appreciated, the fourth embodiment is particularlyadapted for use where the flow of fluid through the pipe union assemblymust be halted when the embodiment is disassembled. Using the teachingsprovided herein, embodiments of the present invention may be devised tohalt the fluid flow from just one or both fitting members usingstructures other than those represented in FIGS. 12 and 13.

G. Summary

It will be appreciated that the above-described embodiments are asignificant advance over the pipe couplings available in the prior art.

As mentioned previously, some of the primary considerations which mustbe implemented when practicing the present invention include the angleof the sealing surfaces, the surface roughness of the sealing surfaces,tolerance of the sealing surface angle, the hardness differential of thesealing surfaces, the coefficient of thermal expansion of the unioncomponents, as well as other considerations which were previouslymentioned or which will be appreciated by those skilled in the art.Importantly, the pipe union assembly of the present invention providesthe advantage of being quickly assembled and disassembled by hand orwith simple tools.

Also of importance is that the present invention provides ametal-to-metal seal which may be used at extremely hot or extremely coldtemperatures. Also, the present invention provides a pipe union whichmay be assembled at the ambient temperature and still maintain a secureseal over a wide range of temperatures and pressures. Furthermore, apipe union made in accordance with the present invention may be reusedmany times due to, among other features, the use of a rigid sealingmember, rather than a flexible sealing member.

Also, the rigid sealing member is extremely resistant to damage causedby over tightening. Embodiments of the present invention also provideprotection to a person disassembling the pipe union by allowing residualpressure to be released in a controlled fashion rather than allowing theresidual pressure to "blow apart" the pipe union. These and otherbenefits are gained by use of the pipe union assemblies of the presentinvention.

Moreover, the present invention may be adapted for use in variousindustries. One described embodiment is particularly adapted forapplications when the flow of fluid through the pipe union must bechecked or halted automatically upon disassembly of the union andreinitiated upon reassembly of the pipe union.

It will be appreciated that the apparatus of the present invention arecapable of being incorporated in the form of a variety of embodiments,only a few of which have been illustrated and described above. Theinvention may thus be embodied in other specific forms without departingfrom its spirit or essential characteristics. The described embodimentsare to be considered in all respects only as illustrative and notrestrictive. The scope of the invention is, therefore, indicated by theappended claims rather than by the foregoing description. All changeswhich come within the meaning and range of equivalency of the claims areto be embraced within their scope.

What is claimed and desired to be secured by United States LettersPatent is:
 1. A pipe union assembly for coupling a first pipe member toa second pipe member, the pipe union comprising:(a) a hollow firstfitting member having a first end, a second end, and means for attachingthe first fitting member at the first end thereof to the first pipemember; (b) a truncated tapered ridge peripherally formed at the secondend of the first fitting member, the truncated tapered ridge having twoopposing flat sides, each of said sides being oriented at an angle in arange from about 6° to about 8° with respect to a central axis of thefirst fitting member; (c) a hollow rigid sealing member having a firsttapered channel peripherally formed on a first end, the first taperedchannel being defined in part by two flat tapered walls, the walls beingoriented with respect to a central axis of the sealing member at anangle which is substantially equal to the angle at which the sides ofthe tapered ridge are oriented with respect to the central axis of thefitting member, the first tapered channel also being configured toreceive in sealing engagement the tapered ridge such that the truncatedtapered ridge does not completely penetrate the first tapered channel;and (d) securing means for selectively applying pressure to the firstfitting member to hold the truncated tapered ridge in sealed engagementwith the first tapered channel such that the sealing engagement ismaintained while the pipe union undergoes thermal cycling.
 2. A pipeunion assembly as defined in claim 1, wherein the rigid sealing membercomprises means for attaching the second end of the rigid sealing memberto a second pipe member.
 3. A pipe union assembly as defined in claim 1,further comprising:(a) a hollow second fitting member having a firstend, a second end, and means for attaching the second fitting member atthe first end thereof to the second pipe member; and (b) a truncatedtapered ridge peripherally formed at the second end of the secondfitting member.
 4. A pipe union assembly as defined in claim 3, whereinthe hollow rigid sealing member further comprises:(a) a second taperedchannel peripherally formed on a second end of the hollow rigid sealingmember, the second tapered channel being configured to receive insealing engagement the tapered ridge formed on the second fitting membersuch that the truncated tapered ridge does not completely penetrate thesecond tapered channel; and (b) wherein the securing means furthercomprises means for selectively applying pressure to the first and thesecond hollow fitting members so as to hold each truncated tapered ridgein sealing engagement with the corresponding first and second taperedchannels.
 5. A pipe union assembly as defined in claim 1, wherein theflat sides of the tapered ridge are fabricated from a material having aBrinell hardness value in a range from about 5 to about 200 Brinellunits different than the Brinell hardness value of a material from whichthe walls of the tapered channel are fabricated, the Brinell units beingmeasured on the Brinell hardness scale.
 6. A pipe union assembly asdefined in claim 1, wherein the flat sides of the tapered ridge arefabricated from a material having a Brinell hardness value in a rangefrom about 10 to about 150 Brinell units different than the Brinellhardness value of a material from which the walls of the tapered channelare fabricated, the Brinell units being measured on the Brinell hardnessscale.
 7. A pipe union assembly as defined in claim 1, wherein thesecuring means comprises:(a) a hollow external sleeve having an interiorsurface with engagement threads positioned on a portion thereof; and (b)the first fitting member having an exterior surface with engagementthreads positioned on a portion thereof and adapted to engage theengagement threads on the external sleeve.
 8. A pipe union assembly asdefined in claim 1, further comprising restraining means for inhibitingthe complete release of the securing means until the sealing engagementbetween the tapered ridge and the tapered channel is broken to allowpressure within the pipe union assembly to be substantially released. 9.A pipe union assembly as defined in claim 1, wherein the sealing memberis fabricated from a material having a coefficient of thermal expansionand the first fitting member is fabricated from a material having acoefficient of thermal expansion, the coefficient of thermal expansionof the sealing member being greater than the coefficient of thermalexpansion of the first fitting member.
 10. A pipe union assembly asdefined in claim 1, wherein the sealing member is fabricated from amaterial having a coefficient of thermal expansion and the first fittingmember is fabricated from a material having a coefficient of thermalexpansion, the coefficient of thermal expansion of the sealing memberbeing less than the coefficient of thermal expansion of the firstfitting member.
 11. A pipe union assembly as defined in claim 1, furthercomprising means for compensating for thermal contraction of the rigidsealing member and the first fitting member so as to maintain the rigidsealing member in sealing engagement with the first fitting member attemperatures lower than the ambient assembly temperature.
 12. A pipeunion assembly as defined in claim 7, further comprising:(a) the sealingmember having an exterior surface defining a annular groove encirclingthe sealing member between the first end and the second end of thesealing member; (b) a channel extending through the external sleeve tocommunicate with the annular groove on the sealing member; and (c) a setscrew selectively advanceable through the channel and into the annulargroove on the sealing member.
 13. A pipe union assembly for providing asealed engagement between a first pipe member and a second pipe member,the pipe union assembly comprising:(a) a hollow first fitting memberhaving a first end, a second end, and means for attaching the firstfitting member at the first end thereof to the first pipe member; (b) atruncated tapered ridge comprising two nonparallel sides, the truncatedtapered ridge peripherally formed at the second end of the first fittingmember, at least one of the nonparallel sides being oriented at an anglein a range from about 2° to about 12° in relation to a central axis ofthe first fitting member; (c) a hollow rigid sealing member having afirst end, a second end, and a tapered channel peripherally formed atthe second end, the tapered channel comprising two nonparallel wallsoriented at an angle in a range from about 2° to about 12° in relationto a central axis of the hollow rigid sealing member, the walls of thetapered channel being configured to sealingly engage the sides of thetruncated tapered ridge, and the walls of the tapered channel also beingsufficiently rigid and having a hardness value in a range from about 5Brinell units to about 200 Brinell units different than a hardness valueof the sides of the truncated tapered ridge such that both the sides ofthe truncated tapered ridge and the walls of the tapered channel resistany substantial macroscopic deformation after the truncated taperedridge is sealingly engaged within the tapered channel and the sealingengagement is maintained as the pipe union assembly is subjected tothermal cycling.
 14. A pipe union assembly as defined in claim 13,wherein the hollow rigid sealing member comprises means for attachingthe second end of the hollow sealing member to the second pipe member.15. A pipe union assembly as defined in claim 14, wherein the means forattaching the second end of the hollow sealing member to the second pipemember comprises:(a) a hollow second fitting member having a first end,a second end, and means for attaching the second fitting member at thefirst end thereof to the second pipe member; and (b) a truncated taperedridge peripherally formed at the second end of the second fittingmember.
 16. A pipe union assembly as defined in claim 15, wherein thehollow rigid sealing member further comprises:(a) a second taperedchannel peripherally formed on the second end of the hollow rigidsealing member, the second tapered channel being configured to receivein sealing engagement the tapered ridge formed on the second fittingmember; and (b) wherein the pipe union assembly further comprisessecuring means for selectively applying pressure to the first and thesecond hollow fitting members so as to hold each truncated tapered ridgein sealing engagement with the corresponding first and second taperedchannels.
 17. A pipe union assembly as defined in claim 13, wherein atleast one of the nonparallel sides of the tapered ridge is oriented atan angle in the range from about 5° to about 9° with respect to thecentral axis of the first fitting member and wherein the side walls ofthe tapered channel are oriented with respect to the central axis of thesealing member at an angle which is substantially equal to the angle atwhich the sides of the tapered ridge are oriented with respect to thecentral axis of the fitting member.
 18. A pipe union assembly as definedin claim 13, further comprising securing means for selectively applyingpressure to the first fitting member to hold the truncated tapered ridgein sealed engagement with the first tapered channel such that thesealing engagement is maintained while the pipe union undergoes thermalcycling.
 19. A pipe union assembly as defined in claim 18, wherein thesecuring means comprises:(a) a hollow external sleeve having an interiorsurface with engagement threads positioned on a portion thereof; and (b)the first fitting member having an exterior surface with engagementthreads positioned on a portion thereof and adapted to engage theengagement threads on the external sleeve.
 20. A pipe union assembly asdefined in claim 13, further comprising restraining means for inhibitingthe release of the securing means until the sealing engagement betweenthe tapered ridge and the tapered channel is broken to allow pressurewithin the pipe union assembly to be substantially released.
 21. A pipeunion assembly comprising:(a) a hollow first fitting member having anexterior surface extending between a first end and an opposing secondend, the first fitting member further comprising a truncated taperedridge peripherally projecting from the second end, the tapered ridgecomprising two nonparallel sides with at least one of the nonparallelsides being oriented at an angle in a range from about 2° to about 12°in relation to a central axis of the first fitting member; (b) a hollowsecond fitting member having an exterior surface extending between afirst end and an opposing second end, the second fitting member furthercomprising a truncated tapered ridge peripherally projecting from thesecond end, the tapered ridge comprising two nonparallel sides with atleast one of the nonparallel sides being oriented at an angle in a rangefrom about 2° to about 12° in relation to the central axis of the firstfitting member; and (c) a hollow rigid sealing member positioned betweenthe tapered ridge of the first fitting member and the tapered ridge ofthe second fitting member, the sealing member comprising:(i) a first endface having an annular tapered channel recessed therein, the taperedchannel comprising two nonparallel walls oriented at an angle in a rangefrom about 2° to about 12° in relation to a central axis of the sealingmember, the walls of the tapered channel being configured to sealinglyengage the tapered ridge of the first fitting member; and (ii) a secondend face having an annular tapered channel recessed therein, the taperedchannel comprising two nonparallel walls oriented at an angle in a rangefrom about 2° to about 12° in relation to the central axis of thesealing member, the walls of the tapered channel being configured tosealingly engage the tapered ridge of the second fitting member, thewalls of each tapered channel being sufficiently rigid and having ahardness value in a range from about 5 Brinell units to about 200Brinell units different than a hardness value for the nonparallel sidesof each tapered ridge such that both the nonparallel sides of eachtapered ridge and the walls of each tapered channel resist anysubstantial macroscopic deformation after each tapered ridge issealingly engaged within each corresponding tapered channel and thesealing engagement is maintained as the pipe union assembly is subjectedto thermal cycling; and (d) securing means for applying pressure to thefirst and second fitting member to hold each tapered ridge in sealedengagement with each corresponding tapered channel such that the sealingengagement is maintained while the pipe union undergoes thermal cycling.22. A pipe union assembly as defined in claim 21, wherein the securingmeans comprises:(a) the first fitting member having an exterior surfacewith a set of engagement threads positioned thereon; (b) the secondfitting member having an exterior surface with an annular ring radiallyextending outward therefrom to an outer diameter; and (c) a tubularsleeve having a first end, an opposing second end, and an interiorsurface defining a passageway longitudinally extending between the firstend and the second end, the interior surface also having:(i) a set ofengagement threads positioned at the first end for complementaryengagement with the engagement threads on the exterior surface of thefirst fitting member; and (ii) an annular lip positioned at the secondend and radially projecting inwards, the annular lip having an innerdiameter smaller than the outer diameter of the annular ring on theexterior surface of the second fitting member.
 23. A pipe union asdefined in claim 22, further comprising a compensating washer positionedbetween the annular ring and the annular lip, the annular ring beingpositioned between the annular lip on the hollow sleeve and the firstend of the hollow sleeve.
 24. A pipe union as defined in claim 22,further comprising:(a) the exterior surface of the second fitting memberdefining an annular groove positioned between the first end and thesecond end of the second fitting member, and (b) an expandably resilientrestraining clip configured to be received within the annular groove onthe second fitting member so as to project above the exterior surface ofthe second fitting member.
 25. A pipe union as defined in claim 22,further comprising:(a) the sealing member having an exterior surfacedefining a annular groove encircling the sealing member between thefirst end face and the second end face; (b) a threaded channel extendingthrough the tubular sleeve to communicate with the annular groove on thesealing member; and (c) a set screw selectively advanceable through thethreaded channel and into the annular groove on the sealing member. 26.A pipe union as defined in claim 22, wherein each tapered ridge and eachtapered channel has an exterior surface machined to at least a 32finish.
 27. A pipe union assembly comprising:(a) a hollow first fittingmember having an exterior surface extending between a first end and anopposing second end, the first fitting member further comprising:(i) atruncated tapered ridge peripherally projecting from the second end, thetapered ridge comprising two nonparallel sides with at least one of thenonparallel sides being oriented at an angle in a range from about 2° toabout 12° in relation to the central axis of the first fitting member;and (ii) a set of engagement threads positioned on a portion of theexterior surface of the first fitting member; (b) a hollow secondfitting member having an exterior surface extending between a first endand an opposing second end, the second fitting member furthercomprising:(i) an annular truncated tapered ridge projecting from thesecond end, the tapered ridge comprising two nonparallel sides with atleast one of the nonparallel sides being oriented at an angle in therange from about 2° to about 12° in relation to a central axis of thefirst fitting member; and (ii) an annular ring encircling and radiallyextending outward from the exterior surface, the annular ring having anouter diameter; (c) a hollow sleeve having a first end, an opposingsecond end, and an interior surface defining a passageway longitudinallyextending between the first end and the second end, the interior surfacealso having:(i) a set of engagement threads positioned at the first endfor complementary engagement with the engagement threads on the exteriorsurface of the first fitting member; and (ii) an annular lip positionedat the second end and radially projecting inwards, the annular liphaving an inner diameter smaller than the outer diameter of the annularring on the exterior surface of the second fitting member; and (d) ahollow rigid sealing member freely positioned within the sleeve betweenthe tapered ridge of the first fitting member and the tapered ridge ofthe second fitting member, the sealing member comprising:(i) a first endface having an annular tapered channel recessed therein, the taperedchannel comprising two nonparallel walls oriented at an angle in a rangefrom about 2° to about 12° in relation to a central axis of the hollowrigid sealing member, the walls of the tapered channel being configuredto sealingly engage the tapered ridge of the first fitting member; and(ii) a second end face having an annular tapered channel recessedtherein, the tapered channel comprising two nonparallel walls orientedat an angle in a range from about 2° to about 12° in relation to thecentral axis of the hollow rigid sealing member, the walls of thetapered channel being configured to sealingly engage the tapered ridgeof the second fitting member, the walls of each tapered channel beingsufficiently rigid and having a hardness value in a range from about 5Brinell units to about 200 Brinell units different than a hardness valuefor the nonparallel sides of each tapered ridge such that both thenonparallel sides of each tapered ridge and the walls of each taperedchannel resist any substantial macroscopic deformation after eachtapered ridge is sealingly engaged within each corresponding taperedchannel and the sealing engagement is maintained as the pipe unionassembly is subjected to thermal cycling.
 28. A pipe union as defined inclaim 27, further comprising a compensating washer positioned betweenthe annular ring and the annular lip, the annular ring being positionedbetween the annular lip on the hollow sleeve and the first end of thehollow sleeve.
 29. A pipe union defined in claim 27, furthercomprising:(a) the exterior surface of the second fitting memberdefining a annular groove positioned between the first end and thesecond end of the second fitting member, and (b) an expandably resilientrestraining clip configured to be received within the annular groove onthe second fitting member so as to project above the exterior surface ofthe second fitting member.
 30. A pipe union as defined in claim 27,further comprising:(a) the sealing member having an exterior surfacedefining a annular groove encircling the sealing member between thefirst end face and the second end face; (b) a threaded channel extendingthrough the tubular sleeve to communicate with the annular groove on thesealing member; and (c) a set screw selectively advanceable through thethreaded channel and into the annular groove on the sealing member.